CN105531135A - Power transmitting apparatus for hybrid vehicle - Google Patents

Power transmitting apparatus for hybrid vehicle Download PDF

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Publication number
CN105531135A
CN105531135A CN201480050391.6A CN201480050391A CN105531135A CN 105531135 A CN105531135 A CN 105531135A CN 201480050391 A CN201480050391 A CN 201480050391A CN 105531135 A CN105531135 A CN 105531135A
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China
Prior art keywords
change gear
gear mechanism
shaft
power
link
Prior art date
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Granted
Application number
CN201480050391.6A
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Chinese (zh)
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CN105531135B (en
Inventor
金田俊树
茨木隆次
安田勇治
田端淳
今村达也
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Toyota Motor Corp
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Toyota Motor Corp
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Publication of CN105531135B publication Critical patent/CN105531135B/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
    • B60K6/405—Housings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/44—Series-parallel type
    • B60K6/445—Differential gearing distribution type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K2006/381—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches characterized by driveline brakes
    • B—PERFORMING OPERATIONS; TRANSPORTING
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    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
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    • B60Y2200/92—Hybrid vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
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    • B—PERFORMING OPERATIONS; TRANSPORTING
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    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S903/00—Hybrid electric vehicles, HEVS
    • Y10S903/902—Prime movers comprising electrical and internal combustion motors
    • Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
    • Y10S903/904—Component specially adapted for hev
    • Y10S903/909—Gearing
    • Y10S903/91—Orbital, e.g. planetary gears
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S903/00—Hybrid electric vehicles, HEVS
    • Y10S903/902—Prime movers comprising electrical and internal combustion motors
    • Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
    • Y10S903/904—Component specially adapted for hev
    • Y10S903/915—Specific drive or transmission adapted for hev
    • Y10S903/917—Specific drive or transmission adapted for hev with transmission for changing gear ratio

Abstract

A power transmitting apparatus includes a transmission gear mechanism (17) and a power split mechanism (4) comprising a first rotation element (8) that is connected to a first input member (125), a second rotation element (6) that is connected to a rotary machine (2), and a third rotation element (7) that is connected to the drive shaft (126) via a first output member (129). The transmission gear mechanism (17) is configured to transmit a torque to the first input member (125) and the first rotation element (8) via a second output member (101). The transmission gear mechanism (17) and the power split mechanism (4) are arranged on the same rotation axis as an output shaft of an engine (1). The transmission gear mechanism (17) and the power split mechanism (4) are arranged in the order of the transmission gear mechanism (17) and the power split mechanism (4) from the side closer to the engine (1). The second output member (101) and the first input member (125) are connected to each other by a spline (101a, 125a) or a serration (101a, 125a).

Description

For the torque transfer of motor vehicle driven by mixed power
Technical field
The present invention relates to a kind of torque transfer be arranged on motor vehicle driven by mixed power, this motor vehicle driven by mixed power comprises multiple drive sources with different power generation principles.
Background technology
Motor vehicle driven by mixed power a kind ofly comprises the following vehicle of multiple drive sources as travelling drive source: described multiple drive source has different power and produces principle, as being become by thermal energy kinetic energy to produce the driving engine of power and to have the whirler of energy regeneration function.Motor vehicle driven by mixed power is a kind of following vehicle: comprise the combustion engine (as spark ignition engine or diesel engine) as drive source and the whirler as drive source (as have the motor of electricity generate function or have the fluid power motor of pressure accumulation function).In addition, motor vehicle driven by mixed power is a kind of following vehicle: by effectively utilizing the characteristic of driving engine and whirler, and it can improve energy efficiency and reduce free air capacity.The example of this motor vehicle driven by mixed power is described in No. 2008-120234th, Japanese Patent Application Publication (JP2008-120234A).
The hybrid driving apparatus described in JP2008-120234A comprises: as the driving engine of drive source, the first motor and the second motor, wherein the first motor has the function that the power by driving engine generates electricity, and the second motor comes to output link outputting power by the electric power produced by the first motor.On the same axis, and power splitting mechanism is arranged between this first motor and this second motor for first motor and the second motor arrangement, and wherein, this power splitting mechanism is by power distribution to the first motor side that exports from driving engine and output link side.In the hybrid driving apparatus described in JP2008-120234A, change engine speed and by transmission of torque to the variable gear facility location of power splitting mechanism between the first motor and the second motor.
No. 2008-265598th, Japanese Patent Application Publication (JP2008-265598A) describes a kind of motor vehicle driven by mixed power comprising power splitting mechanism, and this motor vehicle driven by mixed power comprises driving engine, the first motor, the second motor and has the planetary gear unit of three rotating elements.The motor vehicle driven by mixed power described in JP2008-265598A comprises power-transfer clutch further, the output shaft of this power-transfer clutch stationary engine, can not rotate.First motor is connected to the output shaft of driving engine via power splitting mechanism, and the second motor is connected to drive wheel.The running of driving engine, the first motor, the second motor and power-transfer clutch is controlled based on the propulsive effort required for vehicle.Described motor vehicle driven by mixed power is configured to perform following motor and drives traveling: under the state making power splitting mechanism be used as speed reduction gearing or acceleration mechanism with the output shaft of stationary engine by engaging clutch, not only drive the first motor but also drive the second motor.
No. 2008-265600th, Japanese Patent Application Publication (JP2008-265600A) describes the structure identical with the motor vehicle driven by mixed power described in JP2008-265598A.JP2008-265600A describes: when power-transfer clutch is engaged the bent axle with stationary engine thus the condition that can not rotate is set up, the running of driving engine stops, and use following mapping graph (map) to control the rotation of two motors, wherein, in described mapping graph, based on the speed ratio of accelerator operation amount, the speed of a motor vehicle and change-speed box, be defined for the torque distribution driving two motors most effectively.
The hybrid driving apparatus described in JP2008-120234 has following structure: the change gear mechanism for changing engine speed is added into the structure of the torque transfer for motor vehicle driven by mixed power of prior art, and the motor vehicle driven by mixed power of the prior art comprises driving engine, motor and power splitting mechanism.By applying this structure, depending on required propulsive effort or motoring condition, driving engine can be made to operate with rotating speed more favourable in fuel efficiency.Thus, the energy efficiency of motor vehicle driven by mixed power can be improved.
On the other hand, change gear mechanism comprises gear mechanism and for the power-transfer clutch of controlled variator or drg.Thus, compared with the torque transfer (not having this change gear mechanism) of the motor vehicle driven by mixed power for prior art, the quantity of parts increases or the quantity of installation step increases, to correspond to the interpolation of change gear mechanism.As a result, the assembling of device may may reduce complicated and its capacity rating.
Summary of the invention
The invention provides a kind of torque transfer for motor vehicle driven by mixed power, even when the change gear mechanism of the rotating speed for changing driving engine is added into this structure according to the device of prior art, described torque transfer can simplification device fitting process and boosting productivity.
According to the solution of the present invention, torque transfer has following structure.Described torque transfer is used for motor vehicle driven by mixed power, and wherein said motor vehicle driven by mixed power comprises as the driving engine of drive source and at least one whirler.Described torque transfer comprises power splitting mechanism and change gear mechanism.Described power splitting mechanism is made up of differential apparatus.Described power splitting mechanism is configured to distribute between described drive source and axle drive shaft or synthesize and transferring power.Described differential apparatus comprises three rotating elements.Described three rotating elements comprise: the first rotating element, and it is connected to the first input link; Second rotating element, it is connected to described whirler; And the 3rd rotating element, it is connected to described axle drive shaft via the first output link.Change gear mechanism is configured to the rotating speed of the described driving engine changed via the second input link input.Described change gear mechanism is configured to transmission of torque extremely described first input link and described first rotating element via the second output link.Described change gear mechanism is arranged on the rotation axis identical with the output shaft of described driving engine with described power splitting mechanism.Described change gear mechanism and described power splitting mechanism arrange with the order of described change gear mechanism and described power splitting mechanism in that side of described driving engine from closer.Described second output link and described first input link are connected to each other by spline or sawtooth.
According in torque transfer of the present invention, be arranged between driving engine and power splitting mechanism for the change gear mechanism changing engine speed.In the present invention, the output link of change gear mechanism and the input link of power splitting mechanism are connected to each other by spline or sawtooth.This is a kind of structure as follows: reduce owing to arranging change gear mechanism for the assembling of anti-locking apparatus or capacity rating.Therefore, according to the present invention, when assembling torque transfer, relatively move along rotation axis direction by causing power splitting mechanism and change gear mechanism, power splitting mechanism can easily be connected each other with change gear mechanism, to make transmission of power become possibility.
Housing holds power splitting mechanism and whirler, and is the pith of torque transfer.Particularly, the input link and output link etc. of change gear mechanism, change gear mechanism can come branch's assembling (sub-assemble) to housing as variable gear unit.Thus, by variable gear unit is attached to housing from rotation axis direction, can easily assembling shell and variable gear unit.Variable gear unit holds change gear mechanism, and housing holds power splitting mechanism, whirler etc.In the case, as mentioned above, spline or sawtooth are formed in the connecting bridge between the output link of change gear mechanism and the input link of power splitting mechanism.Thus, the housing holding power splitting mechanism and the variable gear unit holding change gear mechanism can easily and satisfactorily assemble.As a result, assembling or the capacity rating of the torque transfer comprising change gear mechanism and power splitting mechanism can be improved.
Accompanying drawing explanation
With reference to accompanying drawing, hereafter describing the feature of one exemplary embodiment of the present invention, advantage and technology and industry meaning, wherein same Reference numeral represents same element, and wherein:
Fig. 1 is the sketch of the transmission system illustrating the motor vehicle driven by mixed power that the present invention is applied to, and be the figure of the example illustrating transmission system, wherein, in this transmission system, change gear mechanism is made up of the planetary gear unit of single miniature gears, and this transmission system can suitably be arranged on FR formula vehicle;
Fig. 2 is the sketch of the transmission system illustrating the motor vehicle driven by mixed power that the present invention is applied to, and be the figure of the example illustrating transmission system, wherein, in this transmission system, change gear mechanism is made up of the planetary gear unit of single miniature gears, and this transmission system can suitably be arranged on FF formula vehicle;
Fig. 3 is the form that power-transfer clutch, drg and the motor generator operative condition under the operating condition of the transmission system gone out illustrated in Fig. 1, Fig. 2 is shown;
Fig. 4 is the alignment chart of power splitting mechanism in the transmission system gone out illustrated in Fig. 1, Fig. 2 and change gear mechanism, and is illustrate motor vehicle driven by mixed power only by the output of the second motor generator and the figure of the state travelled;
Fig. 5 is the alignment chart of power splitting mechanism in the transmission system gone out illustrated in Fig. 1, Fig. 2 and change gear mechanism, and is illustrate motor vehicle driven by mixed power to use the output of the first motor generator and the second motor generator and the figure of the state travelled;
Fig. 6 is the alignment chart of power splitting mechanism in the transmission system gone out illustrated in Fig. 1, Fig. 2 and change gear mechanism, and be illustrate change gear mechanism be set to high range overdrive gear (O/D) state (height) and motor vehicle driven by mixed power by the output of driving engine and the figure of the state travelled;
Fig. 7 is the alignment chart of power splitting mechanism in the transmission system gone out illustrated in Fig. 1, Fig. 2 and change gear mechanism, and be illustrate change gear mechanism be set to direct connection state (low) and motor vehicle driven by mixed power by the output of driving engine and the figure of the state travelled;
Fig. 8 is the block diagram of the control system illustrating the motor vehicle driven by mixed power that the present invention is applied to;
Fig. 9 is the mapping graph that the variable speed control of the drived control and change gear mechanism illustrating the motor vehicle driven by mixed power that the present invention is applied to uses, and wherein, illustrates that engine drive driving range and motor drive driving range;
Figure 10 is the sketch of the transmission system illustrating the motor vehicle driven by mixed power that the present invention is applied to, and be the figure of the example illustrating transmission system, wherein, in this transmission system, change gear mechanism is made up of the planetary gear unit of double pinion, and this transmission system can suitably be arranged on FR formula vehicle;
Figure 11 is the sketch of the transmission system illustrating the motor vehicle driven by mixed power that the present invention is applied to, and be the figure of the example illustrating transmission system, wherein, in this transmission system, change gear mechanism is made up of the planetary gear unit of double pinion, and this transmission system can suitably be arranged on FF formula vehicle;
Figure 12 is the cutaway view of the structure specifically illustrated according to the torque transfer for motor vehicle driven by mixed power of the present invention, and wherein change gear mechanism is made up of the planetary gear unit of single miniature gears; And
Figure 13 is the cutaway view of the structure specifically illustrated according to the torque transfer for motor vehicle driven by mixed power of the present invention, and wherein change gear mechanism is made up of the planetary gear unit of double pinion.
Detailed description of the invention
Below, the present invention is described in detail with reference to accompanying drawing.Being arranged on according to torque transfer of the present invention has as the driving engine of drive source and whirler (such as, motor) vehicle on, namely, comprise and there is the motor vehicle driven by mixed power that different power produces multiple drive sources of principle, wherein this driving engine is used for thermal energy to become kinetic energy to produce power, and this whirler can regenerated energy.
Spark ignition engine is typically used as the driving engine of motor vehicle driven by mixed power.In addition, the driving engine in the present invention can apply the combustion engine of the fuel used except gasoline, as diesel engine or LPG driving engine.On the other hand, the motor (that is, motor generator) with electricity generate function is typically used as whirler.In addition, the whirler in the present invention can apply the pressure accumulation function had as oil pressure or air pressure pressure motor, can accumulate and release rotate can flywheel etc.
The driving mode that " engine drive driving mode " or " hybrid power (HV) driving mode " that the motor vehicle driven by mixed power that the present invention is applied to is configured to select motor vehicle driven by mixed power to travel by the power exported from driving engine and motor vehicle driven by mixed power travel by the power exported from whirler.Particularly, when motor is used as whirler, motor vehicle driven by mixed power is configured to select " engine drive driving mode " and " motor driving driving mode ", in described " motor driving driving mode ", by carrying out drive motor by the electric power be accumulated in storage battery, make hybrid car travel.
The instance graph of the Power Train of the motor vehicle driven by mixed power that the present invention can be applied to shows in FIG.Example shown in picture in picture is following so-called two electric machine mixed power vehicle Ve: have as the driving engine (ENG) 1 of drive source and the first motor generator (MG1) 2 and these two whirlers of the second motor generator (MG2) 3.Motor vehicle driven by mixed power Ve is configured to: by using power splitting mechanism 4, the power distribution exported from driving engine 1 is passed to the first motor generator 2 side and axle drive shaft 5 side.Motor vehicle driven by mixed power Ve is also configured to: the electric power produced from the first motor generator 2 is supplied to the second motor generator (MG2) 3, and the power using power to export from the second motor generator 3 is added to axle drive shaft 5.
Power splitting mechanism 4 is made up of the modified roll mechanism comprising three rotating elements.Particularly, power splitting mechanism 4 is made up of the planetary gear unit with sun wheel, pinion carrier and internally toothed annulus.In the example gone out in FIG, use the planetary gear unit of single miniature gears.
The planetary gear unit forming power splitting mechanism 4 is arranged on the axis identical with driving engine 1.First motor generator 2 is connected to the sun wheel 6 of planetary gear unit.That is, the rotor 2a of the first motor generator 2 is connected to sun wheel 6.Internally toothed annulus 7 and sun wheel 6 are arranged on concentric circles.The miniature gears engaged with sun wheel 6 and internally toothed annulus 7 is supported by pinion carrier 8 with rotation and revolution.The output shaft 1a of driving engine 1 is connected to pinion carrier 8 via the change gear mechanism 17 treating to describe after a while.One end of transmission shaft 9 is connected to internally toothed annulus 7.The other end of transmission shaft 9 is connected to axle drive shaft 5 and drive wheel 11 via differential gear 10.
The torque exported from the second motor generator 3 can be added into from power splitting mechanism 4 to the torque that transmission shaft 9 and drive wheel 11 transmit.Particularly, the second motor generator 3 is arranged on the rotation axis identical with driving engine 1, and the second motor generator 3 is connected to transmission shaft 9 via train of gears 12.
In the example gone out illustrated in Fig. 1, single file planetary planetary gear unit is used for train of gears 12.The sun wheel 13 forming the planetary gear unit of train of gears 12 is connected to the rotor 3a of the second motor generator 3.Pinion carrier 14 is connected to transmission shaft 9.Internally toothed annulus 15 is fixed to the stationary member 16 as casing, rotating.That is, in train of gears 12, internally toothed annulus 15 is used as retaining element.The pinion carrier 14 being used as output element when sun wheel 13 is used as input element rotates along the direction identical with sun wheel 13 with the rotating speed lower than sun wheel 13.Thus, when the torque inputing to sun wheel 13 being exported from pinion carrier 14, train of gears 12 is used as speed reduction gearing.That is, train of gears 12 is configured to the torque inputted from the second motor generator 3 to sun wheel 13 to strengthen, and by the transmission of torque of increasing to transmission shaft 9.
First motor generator 2 and the second motor generator 3 are connected to storage battery respectively via the controller of such as not shown inverter.First motor generator 2 and the electric current both the second motor generator 3 are controlled, and make to be used as electrical motor or electrical generator.On the other hand, the aperture of throttle gate or the timing of ignition of driving engine 1 can be controlled.Driving engine 1 be configured to control combustion running automatic stopping, starting and restart.
In the motor vehicle driven by mixed power Ve that the present invention is applied to, change gear mechanism 17 is arranged in driving engine 1 and between power splitting mechanism 4 and the first motor generator 2.Change gear mechanism 17 is configured to switch to direct connection state and acceleration mode, that is, high range overdrive gear (O/D) state.In the example gone out in FIG, change gear mechanism 17 is made up of the planetary gear unit 17a of single miniature gears.The pinion carrier 18 of planetary gear unit 17a is connected to the output shaft 1a of driving engine 1.Internally toothed annulus 19 is connected to the pinion carrier 8 of power splitting mechanism 4, to rotate together.Power-transfer clutch C1 for optionally connecting sun wheel 20 and pinion carrier 18 is arranged between sun wheel 20 and pinion carrier 18.Provide for optionally fixing sun wheel 20 so that non-rotary drg B1.Power-transfer clutch C1 and drg B1 can such as be formed by being engaged frictional engagement mechanism by oil pressure.
In change gear mechanism 17, sun wheel 20 and the pinion carrier 18 of planetary gear unit 17a are connected to each other by engaging clutch C1.As a result, whole planetary gear unit 17a rotates as individual, thus realizes the so-called direct connection state of not carrying out acceleration operation and deceleration-operation.By engagement brake B1 engaging clutch C1 again, whole change gear mechanism 17 is fixed as individual, and the rotation of the pinion carrier 8 of power splitting mechanism 4 and driving engine 1 stops.On the other hand, by only engagement brake B1, the sun wheel 20 of change gear mechanism 17 is used as retaining element, and pinion carrier 18 is used as input element.Thus, the internally toothed annulus 19 being used as output element when pinion carrier 18 is used as input element rotates along the direction identical with pinion carrier 18 with the rotating speed higher than pinion carrier 18.Thus, change gear mechanism 17 is used as acceleration mechanism.That is, change gear mechanism 17 is set to O/D state.
The motor vehicle driven by mixed power Ve illustrated in Fig. 1 to be configured to the driving torque exported from drive source via transmission shaft 9 to be passed to axle drive shaft 5 and drive wheel 11.That is, the transmission system that can suitably be arranged on following so-called FR formula motor vehicle driven by mixed power Ve is illustrated: in described FR formula motor vehicle driven by mixed power, drive source is arranged in the front side of vehicle, and propulsive effort produces from trailing wheel.On the other hand, the present invention can be applied in following so-called FF formula motor vehicle driven by mixed power Ve: drive source is arranged in the front side of vehicle, and propulsive effort produces from front-wheel.The instance graph that suitably can be arranged on the transmission system on FF formula vehicle shows in fig. 2.
The motor vehicle driven by mixed power Ve gone out illustrated in Fig. 2 comprises driving engine 1, first motor generator 2 as drive source similar to the example gone out illustrated in Fig. 1 and the second motor generator 3.Motor vehicle driven by mixed power Ve comprises change gear mechanism 17, power splitting mechanism 4 and train of gears 12.Change gear mechanism 17 comprises planetary gear unit 17a, power-transfer clutch C1 and the drg B1 of the single miniature gears similar to the example that Fig. 1 illustrates.The pinion carrier 18 of planetary gear unit 17a is connected to the output shaft 1a of driving engine 1.Internally toothed annulus 19 is connected to the pinion carrier 8 of power splitting mechanism 4.On the other hand, in the example that Fig. 2 illustrates, the internally toothed annulus 7 of power splitting mechanism 4 is connected to driven wheel 25.Train of gears 12 comprises driven wheel 25, countershaft 26, counter drive gear 27, reducing gear 28 and Differential Driving gear 29.
Particularly, countershaft 26 is arranged to the rotation axis parallel with driving engine 1, power splitting mechanism 4 etc.The counter drive gear 27 engaged with driven wheel 25 is attached to countershaft 26, to rotate together.The torque exported from the second motor generator 3 can be added into the torque of transmitting from power splitting mechanism 4 to axle drive shaft 5.That is, the second motor generator 3 is arranged to parallel with countershaft 26, and the reducing gear 28 being connected to its rotor 3a engages with counter drive gear 27.Reducing gear 28 is made up of the gear with the diameter less than counter drive gear 27.Thus, when the torque inputing to reducing gear 28 is passed to countershaft 26 via counter drive gear 27, train of gears 12 is used as speed reduction gearing.That is, train of gears 12 is configured to strengthen the torque exported from the second motor generator 3, and by the transmission of torque of increasing to countershaft 26.
Differential Driving gear 29 is attached to countershaft 26, to rotate together.In the example gone out in fig. 2, internally toothed annulus 30 is formed on the peripheral part of differential gear 10.Differential Driving gear 29 engages with the internally toothed annulus 30 be formed on differential gear 10.Thus, input to power splitting mechanism 4 and from internally toothed annulus 7 export torque and from second motor generator 3 export torque be passed to axle drive shaft 5 and drive wheel 11 via train of gears 12 and differential gear 10.In fig. 2, for the object being convenient to accompanying drawing preparation, the right side in Fig. 2 is partial in the position of differential gear 10.
The driving mode of the motor vehicle driven by mixed power Ve gone out illustrated in Fig. 1, Fig. 2 or be in retreats power-transfer clutch C1 in motoring condition and the joint of drg B1 and the operative condition of release position and the first motor generator 2 and the second motor generator 3 and is shown in the form of Fig. 3.Be briefly described about operative condition, " EV " in Fig. 3 represents that motor drives driving mode.In " single motor driving driving mode ", power-transfer clutch C1 and drg B1 discharges.Second motor generator 3 is used as electrical motor (M), and the first motor generator 2 is used as electrical generator (G).In the case, the first motor generator 2 can tickover.This constitution diagram is shown in the alignment chart of Fig. 4.When causing engine braking effect in " single motor driving driving mode ", one of power-transfer clutch C1 and drg B1 are engaged, and the rotating speed of internally toothed annulus 7 in power splitting mechanism 4 is suppressed.
Drive in " the Dual-motors Driving driving mode " of driving mode at motor, both the first motor generator 2 and the second motor generator 3 are used as electrical motor.In order to the transmission of torque will exported from the first motor generator 2 is to axle drive shaft 5, power-transfer clutch C1 and drg B1 is engaged, and the pinion carrier 8 of power splitting mechanism 4 is fixed, so that non rotating.In this case, the ratio of number of teeth of rotating element is set to and makes power splitting mechanism 4 be used as speed reduction gearing.Thus, in the case, the torque exported from the first motor generator 2 is strengthened, and is passed to transmission shaft 9 from the internally toothed annulus 7 of power splitting mechanism 4.This constitution diagram is shown in the alignment chart of Fig. 5.
On the other hand, " HV " in the form of Fig. 3 represents the hybrid power operative condition that driving engine 1 operates.Motor vehicle driven by mixed power Ve with in or the high speed of a motor vehicle and with underloading travel state under, change gear mechanism 17 is set to O/D state (height).That is, releasing clutch C1, and engagement brake B1.This constitution diagram is shown in the alignment chart of Fig. 6.In this case, as mentioned above, engine speed is controlled to the good rotating speed of fuel efficiency by the first motor generator 2.In the case, the electric power produced by causing the first motor generator 2 to be used as electrical generator is fed into the second motor generator 3.As a result, the second motor generator 3 is used as electrical motor and exports driving torque.When needing large propulsive effort, as when the low speed of a motor vehicle during accelerator operation amount increase, change gear mechanism 17 is controlled so as to direct connection state (low).That is, engaging clutch C1, and discharge drg B1.As a result, whole change gear mechanism 17 rotates as individual.This constitution diagram is shown in the alignment chart of Fig. 7.In the case, similar in appearance to O/D state (height), the first motor generator 2 is used as electrical generator, and the second motor generator 3 is used as electrical motor.
There is provided following electronic control unit (ECU) 21: the running carrying out driving engine 1 controls, the running of the first motor generator 2 and the second motor generator 3 controls and the joint of power-transfer clutch C1 and drg B1 and release control.The control system of ECU21 is shown in the block diagram of Fig. 8.
ECU21 comprises the control unit of engine (E/G-ECU) 24 controlling overall the hybrid power control unit (HV-ECU) 22, the motor generator control unit (MG-ECU) 23 controlling the first motor generator 2 and the second motor generator 3 and the control driving engine 1 that travel.Control unit 22,23,24 is configured to: be used as the microcomputer of main body, use input data and previously stored data to carry out calculating and export the result of calculation as control command signal.
Along with input data input to ECU21, such as, the rotating speed (rotating speed of output shaft) of the rotating speed of the rotating speed of the speed of a motor vehicle, accelerator operation amount, the first motor generator 2, the second motor generator 3, internally toothed annulus 7, the rotating speed of driving engine 1 and the SOC of storage battery input to HV-ECU22.Along with control signal exports from ECU21, such as, the oil pressure bid value PB1 of the torque command value of the torque command value of the first motor generator 2, the second motor generator 3, the torque command value of driving engine 1, the oil pressure bid value PC1 of power-transfer clutch C1 and drg B1 exports from HV-ECU22.
The torque command value of the first motor generator 2 and the torque command value of the second motor generator 3 are input to MG-ECU23 as control data.MG-ECU23 is configured to: calculate based on torque command value, and exports the current command signal of the first motor generator 2 and the second motor generator 3.Engine torque command signal is input to E/G-ECU24 as control data.E/G-ECU24 is configured to: calculate based on engine torque command value, and exports for the throttle opening amount signal of electronic throttle (not shown), for controlling the ignition signal etc. of timing of ignition.
As mentioned above, driving engine 1, first motor generator 2 and the second motor generator 3 that form the drive source of motor vehicle driven by mixed power Ve have different tractive performancies or different drive performances.Such as, driving engine 1 can from low torque and lower speed range to operate in the wide in range operating range of high speed range to high torque (HT).In the high operating range to a certain extent of torque and rotational speed, the energy efficiency of driving engine 1 becomes better.By contrast, the first motor generator 2 has the characteristic exporting large torque at slow speed of revolution, to carry out the control regulating the rotating speed of driving engine 1 or the crankshaft degree when driving engine 1 stops etc., and output drive strength.Second motor generator 3 has its characteristic that can operate with the rotating speed higher than the first motor generator 2, to export torque to drive wheel 11, and maximum torque is less than the first motor generator 2.
Using driving engine 1, first motor generator 2 and the second motor generator 3 as in the motor vehicle driven by mixed power Ve of drive source, drive source is used to improve energy efficiency or fuel efficiency effectively.Namely, as mentioned above, depend on the driving conditions of motor vehicle driven by mixed power Ve, " motor driving driving mode " that " engine drive driving mode " that vehicle travels by the output of driving engine 1 and vehicle travel by the output of at least one in the first motor generator 2 and the second motor generator 3 is selected and is set.
The operating range of setting driving mode is shown in the mapping graph of Fig. 9.Fig. 9 is the figure of the operating range illustrating motor vehicle driven by mixed power Ve, and wherein, the speed of a motor vehicle is set as horizontal shaft, and required propulsive effort is set as vertical axes.The scope represented by Reference numeral I is the engine drive driving range performing " engine drive driving mode ", and the scope II represented by Reference numeral is the motor driving driving range performing " motor driving driving mode ".In engine drive driving range I, the threshold value T be set as follows: described threshold value is used for separately change gear mechanism 17 and is controlled so as to the scope that the scope of direct connection state (low) and change gear mechanism 17 are controlled so as to O/D state (height).Depend on the propulsive effort needed for motor vehicle driven by mixed power Ve, select and the driving mode of setting change gear mechanism 17 and speed change level (transmissiongearstage).Such as, as represented by the arrow a in Fig. 9, the operation point determined by the speed of a motor vehicle and required propulsive effort moves to the scope of O/D state (height) from the scope of direct connection state (low), thus carries out the variable speed control from direct connection state (low) to O/D state (height) of change gear mechanism 17.ECU21 is configured to: control the switching of the driving mode determined by the change in operating range, or controls the switching of the speed change level of change gear mechanism 17.
In the motor vehicle driven by mixed power Ve gone out illustrated in Fig. 1, Fig. 2, change gear mechanism 17 is made up of single file planetary planetary gear unit 17a.On the other hand, in the present invention, change gear mechanism 17 can be made up of double planetary planetary gear unit.The example that change gear mechanism 17 is made up of double planetary planetary gear unit and the instance graph of transmission system that can suitably be arranged on FR formula vehicle show in Fig. 10.
The motor vehicle driven by mixed power Ve illustrated in motor vehicle driven by mixed power Ve and the Fig. 1 illustrated in Figure 10 is different to be: the structure of change gear mechanism 17 and change gear mechanism 17 and the annexation between driving engine 1 and the first motor generator 2.Particularly, in the example illustrated in Fig. 10, change gear mechanism 17 is made up of the planetary gear unit 17b of double pinion.The internally toothed annulus 31 of planetary gear unit 17b is connected to the output shaft 1a of driving engine 1.The pinion carrier 32 of planetary gear unit 17b is connected to the pinion carrier 8 of power splitting mechanism 4, to rotate together.The side of the pinion carrier 32 in the example illustrated in Figure 10 engages with sun wheel 33, and opposite side engages with internally toothed annulus 31, and be engaged with each other two miniature gearss are supported, and makes rotation and revolution.Power-transfer clutch C1 for optionally connecting sun wheel 33 and pinion carrier 32 is arranged between sun wheel 33 and pinion carrier 32.Arrange and be used for optionally fixing sun wheel 33 so that non-rotary drg B1.
In change gear mechanism 17 in the example illustrated in Fig. 10, similar in appearance to the example that Fig. 1 illustrates, sun wheel 33 and the pinion carrier 32 of planetary gear unit 17b are connected to each other by engaging clutch C1.As a result, whole planetary gear unit 17b rotates as individual, and realizes the so-called direct connection state of not carrying out acceleration operation and deceleration-operation.By engagement brake B1 engaging clutch C1 again, whole change gear mechanism 17 is fixed as individual, and the rotation of the pinion carrier 8 of power splitting mechanism 4 and driving engine 1 stops.On the other hand, in the change gear mechanism 17 in the example that Figure 10 illustrates, by only engagement brake B1, the sun wheel 33 of change gear mechanism 17 is used as retaining element, and internally toothed annulus 31 is used as input element.Thus, the pinion carrier 32 being used as output element when internally toothed annulus 31 is used as input element rotates along the direction identical with internally toothed annulus 31 with the rotating speed higher than internally toothed annulus 31.Thus, change gear mechanism 17 is used as acceleration mechanism.That is, change gear mechanism 17 is set to O/D state (height).
The example that change gear mechanism 17 is made up of double planetary planetary gear unit and the instance graph of transmission system that can suitably be arranged on FF formula vehicle show in fig. 11.The motor vehicle driven by mixed power Ve illustrated in diagram motor vehicle driven by mixed power Ve and Fig. 2 is in fig. 11 different to be: the structure of change gear mechanism 17 and change gear mechanism 17 and the annexation between driving engine 1 and the first motor generator 2.The change gear mechanism 17 be made up of the planetary gear unit 17b of double pinion and change gear mechanism 17 identical with the transmission system of the motor vehicle driven by mixed power Ve illustrated in the annexation between driving engine 1 and the first motor generator 2 and Figure 10.
As mentioned above, according to of the present invention in the torque transfer TM of motor vehicle driven by mixed power, be arranged between driving engine 1 and power splitting mechanism 4 for the change gear mechanism 17 changing the rotating speed of driving engine 1.Thus, with of the prior art do not have change gear mechanism 17 for motor vehicle driven by mixed power torque transfer compared with, fitting work is complicated, and the quantity of assembly process along with the parts of change gear mechanism 17 quantity increase and increase.
Thus, according to of the present invention in the torque transfer of motor vehicle driven by mixed power, even if change gear mechanism 17 is added in structure of the prior art, also can make the assembling of device simplify and can boost productivity.Concrete structure instance graph shows in fig. 12.The torque transfer TM illustrated in Figure 12 corresponds to the structure of the transmission system illustrated in Fig. 1, Fig. 2.That is, change gear mechanism 17 is made up of the planetary gear unit 17a of single miniature gears.
Torque transfer TM comprises change gear mechanism 17, first motor generator 2 and power splitting mechanism 4.In fig. 12, change gear mechanism 17, first motor generator 2 and power splitting mechanism 4 from closer in not shown that side of driving engine 1 (that is, from the front of torque transfer TM) with the order arrangement of change gear mechanism 17, first motor generator 2 and power splitting mechanism 4.Below, " front " and " front side " represents the left side in Figure 12 or Figure 13, and " rear " and " rear side " represents the right side in Figure 12 or Figure 13.
Change gear mechanism 17 comprises planetary gear unit 17a, power-transfer clutch C1, drg B1, the input shaft 100 of single miniature gears and exports flange 101.Power-transfer clutch C1 comprises: friction member 102, and it is connected to each other for the sun wheel 20 and pinion carrier 18 making planetary gear unit 17a; And hydraulic actuator 103 and retracing spring 104, it operates for causing friction member 102, power-transfer clutch C1 is controlled to engagement state and release position.Hydraulic actuator 103 is supplied to the oil pressure for engaging clutch C1 via the oil circuit 116 treating to describe after a while.On the other hand, drg B1 comprises: friction member 105, and it is for the sun wheel 20 of fixing planetary gear unit 17a, so that non rotating; And hydraulic actuator 106 and retracing spring 107, it operates for causing friction member 105, drg B1 is controlled to engagement state and release position.Hydraulic actuator 106 is supplied to the oil pressure for engagement brake B1 via the oil circuit 117 treating to describe after a while.
Protecgulum 108 for holding planetary gear unit 17a, power-transfer clutch C1, drg B1 and input shaft 100 is set.Under the state of intactly assembling torque transfer TM, protecgulum 108 is protection face components to the part of driving engine 1.In the torque transfer TM that Figure 12 illustrates, planetary gear unit 17a, power-transfer clutch C1, drg B1, input shaft 100 and output flange 101 are arranged in the inside of protecgulum 108.
Particularly, hydraulic actuator 103, retracing spring 104, hydraulic actuator 106 and retracing spring 107 are arranged in the front side in protecgulum 108, that is, in that side (on left side in fig. 12) being close to not shown driving engine 1 in fig. 12.Planetary gear unit 17a is arranged on the internal side diameter at hydraulic actuator 103,106 and retracing spring 104,107 rear.
In the inner peripheral portion of the sun wheel 20 of planetary gear unit 17a, the input shaft 100 as the input link of change gear mechanism 17 is arranged to rotate relative to sun wheel 20.Input shaft 100 is supported by needle bearing 109 and axle sleeve 128, wherein this needle bearing is arranged in the inner peripheral portion of the through hole 108a be formed in protecgulum 108, and this axle sleeve is arranged in the inner peripheral portion of the counterbore in the input shaft 125 being formed at the power splitting mechanism 4 treating to describe after a while.
The flange 113 rotated together with input shaft 100 is formed in input shaft 100, and the pinion carrier 18 of planetary gear unit 17a is connected to flange 113, to rotate together.That is, input shaft 100 and pinion carrier 18 are connected to each other, to rotate together.The front end of input shaft 100 is given prominence to, input shaft 100 to be connected to via vibration damper mechanism (not shown) the output shaft 1a of driving engine 1 from through hole 108a.The rear end of input shaft 100 is supported by the input shaft 125 of the power splitting mechanism 4 treating to describe after a while.
In the peripheral part of the rear end of input shaft 100, export flange 101 and be arranged on the rear side of flange 113.Export the output link that flange 101 is used as change gear mechanism 17, and be arranged to rotate relative to input shaft 100.Export flange 101 to be supported by thrust baring 114 and thrust baring 115, wherein this thrust baring 114 is arranged in and exports between flange 101 and flange 113, and this thrust baring 115 is arranged in and exports flange 101 and treat that MG1 described later covers between 118.
The internally toothed annulus 19 of planetary gear unit 17a is connected to and exports flange 101, to rotate together.Following splined hole 101a is formed in the rear end exporting flange 101: this splined hole is used for output flange 101 to be connected to the input shaft 125 treating power splitting mechanism 4 described later.That is, castellated shaft 125a is formed in the front end place of the input shaft 125 of power splitting mechanism 4, and output flange 101 and input shaft 125 are fitted to each other by spline.
The friction member 102 of power-transfer clutch C1 is arranged in the outer circumferential side of hydraulic actuator 103, retracing spring 104 and planetary gear unit 17a.A part for friction member 102 is connected to the sun wheel 20 of planetary gear unit 17a, to rotate together.The other parts of friction member 102 are connected to the pinion carrier 18 of planetary gear unit 17a, to rotate together.The friction member 105 of drg B1 is arranged in the outer circumferential side of power-transfer clutch C1.A part for friction member 105 is connected to the sun wheel 20 of planetary gear unit 17a, to rotate together.The other parts of friction member 105 are fixed to the stationary member 16 being formed in protecgulum 108 inside.
Be formed in protecgulum 108 for the oil circuit 116 to power-transfer clutch C1 supply engagement oil and the oil circuit 117 for supplying engagement oil to drg B1.Such as, by carrying out Drilling operation to the position of three in the example illustrated in Figure 12, oil circuit 116 can easily be formed.Similarly, such as, by carrying out Drilling operation to three positions, oil circuit 117 can easily be formed.Oil circuit 116 and oil circuit 117 are configured to: by protecgulum 108 being assembled to MG1 lid 118 and housing 122, are connected to be formed in treat that MG1 described later covers the supply oil circuit 122b in 118.Supply oil circuit 122b is supplied to the oil pressure for power-transfer clutch C1 and drg B1 from valve body (not shown) side.
Form the component of change gear mechanism 17, as planetary gear unit 17a, power-transfer clutch C1, drg B1 and input shaft 100, be received and be assemblied in protecgulum 108.Under the state of component assembling forming change gear mechanism 17, MG1 lid 118 is attached to the peristome on the rear side of protecgulum 108.Such as, in fig. 12, protecgulum 108 and MG1 lid 118 are fixed to individual by multiple screw 119 to diagram.The through hole 118a identical with protecgulum 108 is formed in MG1 and covers in 118.In a part of through hole 118a, the input shaft 100 of change gear mechanism 17 and treat that the input shaft 125 of power splitting mechanism 4 described later is connected to each other, relatively to rotate, and the output flange 101 of change gear mechanism 17 and treat that the input shaft 125 of power splitting mechanism 4 described later passes through spline fitted.
MG1 lid 118 is formed along the shape of the end in the front (left side in Figure 12) of the first motor generator 2.Thus, a part for the peripheral part of MG1 lid 118 is formed as corresponding with the front end of the coil-end 2b of the first motor generator 2, and the central part being formed with the MG1 lid 118 of through hole 118a has the shape of the inner peripheral portion invading coil-end 2b or stator 2c.That is, as illustrated in the cutaway view of Figure 12, the central part of MG1 lid 118 is outstanding to the right side in Figure 12, and through hole 118a is positioned in the inner peripheral portion of the first motor generator 2.Thus, in the inner peripheral portion of the first motor generator 2, the output flange 101 of change gear mechanism 17 and the input shaft 125 of power splitting mechanism 4 are connected to each other by spline.
So, according in torque transfer TM of the present invention, use the space of the inner peripheral portion of the first motor generator 2, effectively arrange change gear mechanism 17 and power splitting mechanism 4.Thus, the whole length on the rotation axis of torque transfer TM can be shortened, and the minimizing in the size of torque transfer TM and weight can be completed.
In the example illustrated in fig. 12, the friction member 105 that space 108b is formed in drg B1 to the peripheral part of stationary member 16 and the inner peripheral portion of protecgulum 108 between.Space 108b is effectively as the oil return path of oil or the oil tank that are fed into change gear mechanism 17.
Ball-bearing casing 120 for the front end supplying the rotor 2a of the first motor generator 2 is attached to the side surface on the rear side of MG1 lid 118.Particularly, the outer ring 120a of ball-bearing casing 120 is fixed to MG1 lid 118.Be attached to by the MG1 being fixed to individual with protecgulum 108 is covered 118 the housing 122 treating accommodation first motor generator 2 described later, rotor 2a is incorporated to the inner ring 120b of ball-bearing casing 120.End on the rear side of rotor 2a is by treating that ball-bearing casing 124 described later supports.
As mentioned above, forming the component of change gear mechanism 17, as planetary gear unit 17a, power-transfer clutch C1, drg B1 and input shaft 100, when to be incorporated in protecgulum 108 and to cover with MG1 lid 118, change gear mechanism 17 is formed as individual unit.That is, the change gear mechanism 17 in the present invention can be formed as the variable gear unit covered with protecgulum 108 and MG1 lid 118, and variable gear unit can be counted as subcomponent.
Housing 122 for holding the first motor generator 2, magslip 121 (resolver) etc. is arranged in the rear side of the protecgulum 108 and MG1 lid 118 holding change gear mechanism 17.That is, the change gear mechanism 17 that holds described above covers with the protecgulum 108 and MG1 that form variable gear unit the front side that 118 are fixed to housing 122.Such as, as illustrated in figure 12, protecgulum 108, MG1 lid 118 and housing 122 are fixed to one by multiple screw 123.
Housing 122 is to front openings, that is, MG1 covers 118 sides (left side in Figure 12), and magslip 121 is attached to the inside of the sidewall portion 122a on rear side of housing 122.Through hole is formed in sidewall portion 122a, and ball-bearing casing 124 is attached to the inner peripheral portion of through hole.The stator 2c of the first motor generator 2 is fixed to the inside of the housing 122 on front side of magslip 121.
The rotor 2a of the first motor generator 2 inserts the inner peripheral portion of stator 2c.As described above, by housing 122, protecgulum 108 and MG1 lid 118 is assembled into individual, the front end of rotor 2a is supported on MG1 lid 118 by ball-bearing casing 120.On the other hand, the rear end of rotor 2a is supported on housing 122 by ball-bearing casing 124.Following splined hole 2d is formed on the rear end of rotor 2a: this splined hole is used for the sun wheel 6 rotor 2a being connected to power splitting mechanism 4, to make transmission of power become possibility.That is, castellated shaft 127a be formed in as individual with treat in the flange 127 that the sun wheel 6 of power splitting mechanism 4 described later is connected, and rotor 2a and flange 127 pass through spline fitted.
Power splitting mechanism 4 is arranged in the housing 122 of accommodation first motor generator 2.Power splitting mechanism 4 is made up of the planetary gear unit of single miniature gears described above, and comprise to connect with its pinion carrier 8 in case together with the input shaft 125 that rotates and connect with its internally toothed annulus 7 so as together with the output shaft 126 that rotates.Flange 127 is connected to the sun wheel 6 of power splitting mechanism 4, to rotate together.Castellated shaft 127a is formed on the peripheral part of the front end of flange 127.The rotor 2a (splined hole 2d is formed in wherein) of flange 127 and the first motor generator 2 is fitted to each other by spline.That is, the sun wheel 6 of power splitting mechanism 4 is connected to the rotor 2a of the first motor generator 2 by spline, to rotate together.
Input shaft 125 inserts in the inner peripheral portion of sun wheel 6 and flange 127, to rotate relative to the sun wheel 6 of power splitting mechanism 4 and flange 127.Part on the front side of input shaft 125 is given prominence to from flange 127, and from the inner peripheral portion of the outstanding partial insertion rotor 2a of flange 127, to rotate relative to rotor 2a.Castellated shaft 125a is formed on the peripheral part of the front end of input shaft 125.The output flange 101 of input shaft 125 and change gear mechanism 17 is fitted to each other by spline, and wherein splined hole 101a is formed in this output flange.That is, as the output flange 101 of the output link of change gear mechanism 17 be connected to each other by spline, to rotate together as the input shaft 125 of the input link of power splitting mechanism 4.Output flange 101 and input shaft 125 are connected to each other by replacing the sawtooth of spline.
Following counterbore is formed on the front end of input shaft 125: this counterbore for supporting the end at the rear (right side in Figure 12) of the input shaft 100 of change gear mechanism 17, relatively to rotate.Axle sleeve 128 is formed between the rear end of input shaft 100 and the counterbore at front end place being formed in input shaft 125.
The flange 129 rotated together with output shaft 126 is formed in the front end place of output shaft 126, and the internally toothed annulus 7 of power splitting mechanism 4 is connected to flange 129, to rotate together.That is, output shaft 126 is connected with internally toothed annulus 7, to rotate together.On the other hand, the rear end of output shaft 126 is connected to not shown transmission shaft 9 in fig. 12, to rotate together.Part on the rear side of output shaft 126 is supported on the casing 130 that is attached on rear side of housing 122.That is, through hole is formed in the sidewall portion 130a on front side of casing 130, and in the through hole of partial insertion sidewall portion 130a on the rear side of output shaft 126.Output shaft 126 is supported in the inner peripheral portion of the through hole of sidewall portion 130a.
Following counterbore is formed in the front end place of output shaft 126: this counterbore is used for the rear end of the input shaft 125 of supporting motive force distributor gears 4, relatively to rotate.Axle sleeve 131 is arranged between the rear end of input shaft 125 and the counterbore at front end place being formed in output shaft 126.
The internally toothed annulus 7 that example describes power splitting mechanism 4 is connected to the structure of transmission shaft 9 via output shaft 126, that is, be applied to the transmission system on the FR formula vehicle that can suitably be arranged on to go out illustrated in Fig. 1 according to torque transfer TM of the present invention.On the other hand, when being applied to the transmission system on the FF formula vehicle that can suitably be arranged on to go out illustrated in Fig. 2 according to torque transfer TM of the present invention, the internally toothed annulus 7 of power splitting mechanism 4 is connected to the driven wheel 25 forming train of gears 12 via output shaft 126, to rotate together.Other structure can be identical with the example gone out illustrated in Figure 12.
Figure 13 illustrates another structure example according to torque transfer of the present invention.The transmission system gone out illustrated in torque transfer TM and Figure 10, Figure 11 of going out illustrated in Figure 13 is corresponding.That is, change gear mechanism 17 is made up of the planetary gear unit 17b of double pinion.
In fig. 13, torque transfer TM comprises change gear mechanism 17, first motor generator 2 and power splitting mechanism 4, and this is similar in appearance to the structure gone out illustrated in Figure 12.In fig. 13, from being close to not shown that side of driving engine 1, that is, from the front of torque transfer TM, change gear mechanism 17, first motor generator 2 and power splitting mechanism 4 arrange with this order.
In the structure gone out illustrated in Figure 13, change gear mechanism 17 is made up of planetary gear unit 17b, the power-transfer clutch C1 of double pinion, drg B1, input shaft 200 and tween drive shaft 201.Power-transfer clutch C1 comprises: friction member 202, and it is connected to each other for the sun wheel 33 and pinion carrier 32 making planetary gear unit 17b; And hydraulic actuator 203 and retracing spring 204, it operates for causing friction member 202, power-transfer clutch C1 is controlled to engagement state and release position.Hydraulic actuator 203 is supplied to the oil pressure for engaging clutch C1 via the oil circuit 218 treating to describe after a while.On the other hand, drg B1 comprises: friction member 205, and it is for the sun wheel 33 of fixing planetary gear unit 17b, so that non rotating; And hydraulic actuator 206 and retracing spring 207, it operates for causing friction member 205, drg B1 is controlled to engagement state and release position.Hydraulic actuator 206 is supplied to the oil pressure for engagement brake B1 via the oil circuit 219 treating to describe after a while.
Protecgulum 208 for holding planetary gear unit 17b, power-transfer clutch C1, drg B1 and input shaft 200 is set.Under the state of intactly assembling torque transfer TM, protecgulum 208 is protection face components to the part of driving engine 1.In the torque transfer TM that Figure 13 illustrates, planetary gear unit 17b, power-transfer clutch C1, drg B1, input shaft 200 and tween drive shaft 201 are arranged in the inside of protecgulum 208.
Particularly, planetary gear unit 17b is arranged on the front side of protecgulum 208, that is, in that side (left side in Figure 13) being close to not shown driving engine 1 in fig. 13.In the inner peripheral portion of the sun wheel 33 of planetary gear unit 17b, the input shaft 200 as the input link of change gear mechanism 17 is arranged to rotate relative to sun wheel 33 and tween drive shaft 201.Input shaft 200 is supported by needle bearing 209 and axle sleeve 210, and wherein needle bearing is arranged in the inner peripheral portion of the through hole 208a be formed in protecgulum 208, this axle sleeve be arranged in be formed at the tween drive shaft 201 treating to describe after a while inner peripheral portion on.Hydraulic actuator 203, retracing spring 204, hydraulic actuator 206 and retracing spring 207 are attached to the rear side of planetary gear unit 17b.
The flange 211 rotated together with input shaft 200 is formed in input shaft 200, and the internally toothed annulus 31 of planetary gear unit 17b is connected to flange 211, to rotate together.That is, input shaft 200 and internally toothed annulus 31 are connected to each other, to rotate together.The front end of input shaft 200 is given prominence to, input shaft 200 to be connected to via vibration damper mechanism (not shown) the output shaft 1a of driving engine 1 from through hole 208a.As aftermentioned, the rear end of input shaft 200 is supported by tween drive shaft 201.In the part of rear side from the flange 211 of input shaft 200, there is the external diameter less than other parts, so that insertion is formed in the counterbore in tween drive shaft 201.
Except input shaft 200, the tween drive shaft 201 as the output link of change gear mechanism 17 is arranged in the inner peripheral portion of sun wheel 33 of planetary gear unit 17b, to rotate relative to input shaft 200 and sun wheel 33.Tween drive shaft 201 on rear side of input shaft 200 on be arranged on the rotation axis identical with input shaft 200.Tween drive shaft 201 is supported by needle bearing 215 and needle bearing 216, and wherein this needle bearing 215 is arranged in the inner peripheral portion of the through hole 217a be formed in MG1 lid 217, and this needle bearing 216 is arranged in the inner peripheral portion of the rotor 2a of the first motor generator 2.
The pinion carrier 32 of planetary gear unit 17b is connected to tween drive shaft 201, to rotate together.Following counterbore is formed in the front end place of tween drive shaft 201: the minor diameter of this counterbore on the rear side supporting input shaft 200, relatively to rotate.Axle sleeve 210 is formed between the rear end of input shaft 200 and the counterbore at front end place being formed in tween drive shaft 201.Following splined hole 201a is formed in the rear end of tween drive shaft 201: this splined hole for connecting the input shaft 125 of tween drive shaft 201 and power splitting mechanism 4, to make transmission of power become possibility.That is, castellated shaft 125a is formed in the front end place of the input shaft 125 of power splitting mechanism 4, and tween drive shaft 201 and input shaft 125 are fitted to each other by spline.Thus, the tween drive shaft 201 as the output link of change gear mechanism 17 and the input shaft 125 as the input link of power splitting mechanism 4 are connected to each other by spline, to rotate together.Tween drive shaft 201 and input shaft 125 are connected to each other by replacing the sawtooth of spline.
The friction member 202 of power-transfer clutch C1 is arranged on the peripheral part of hydraulic actuator 203, retracing spring 204 and planetary gear unit 17b.A part for friction member 202 is connected to the sun wheel 33 of planetary gear unit 17b, to rotate together.The other parts of friction member 202 are connected to the pinion carrier 32 of planetary gear unit 17b, to rotate together.The friction member 205 of drg B1 is arranged on the peripheral part of power-transfer clutch C1.A part for friction member 205 is fixed to the stationary member 16 be formed in MG1 lid 217.
Form the component of change gear mechanism 17, be received as planetary gear unit 17b, power-transfer clutch C1, drg B1, input shaft 200 and tween drive shaft 201 and be assemblied in protecgulum 208.When assembling the component forming change gear mechanism 17, MG1 lid 217 is attached to the peristome on the rear side of protecgulum 208.Such as, as illustrated in figure 13, protecgulum 208 and MG1 lid 217 are fixed to individual by multiple screw 119.The through hole 217a same with protecgulum 208 is formed in MG1 and covers in 217.Tween drive shaft 201 inserts in the inner peripheral portion of through hole 217a.The rear end (having the splined hole 201a be formed in wherein) of tween drive shaft 201 is given prominence to side backward from through hole 217a, so that in the inner peripheral portion of the rotor 2a of the first motor generator 2, by spline fitted to the input shaft 125 of power splitting mechanism 4.
MG1 lid 217 is formed along the end shape in the front (left side in Figure 13) of the first motor generator 2.Thus, the part of the peripheral part of MG1 lid 217 is formed as corresponding with the front end of the coil-end 2b of the first motor generator 2, and the central part (having the through hole 217a be formed in wherein) of MG1 lid 217 has the shape of the inner peripheral portion invading coil-end 2b or stator 2c.That is, as illustrated in the cutaway view of Figure 13, the central part of MG1 lid 217 is outstanding to the right side in Figure 13, and through hole 217a is positioned in the inner peripheral portion of the first motor generator 2.Thus, in the inner peripheral portion of the first motor generator 2, the tween drive shaft 201 of change gear mechanism 17 is connected to each other by spline with the input shaft 125 of power splitting mechanism 4.
In the example gone out illustrated in Figure 13, similar in appearance to the example gone out illustrated in Figure 12, according in torque transfer TM of the present invention, effectively utilize the space of the inner peripheral portion of the first motor generator 2, arrange change gear mechanism 17 and power splitting mechanism 4.Thus, the whole length of torque transfer TM on rotation axis direction can be shortened, and the reduction in the size of torque transfer TM and weight can be realized.
In the example gone out illustrated in Figure 13, be formed in MG1 lid 217 for the oil circuit 218 that engagement oil is supplied to power-transfer clutch C1 and the oil circuit 219 that is used for engagement oil to be supplied to drg B1.By the tubular member of the corresponding reservation shape of shape that is fixing or that keep being formed as cover with MG1 217, oil circuit 218 is formed to the inner surface (left side in Figure 13) that MG1 covers 217.On the other hand, such as, by carrying out Drilling operation to three positions, oil circuit 219 can easily be formed.By assembling protecgulum 208, MG1 lid 217 and housing 122, oil circuit 218 and oil circuit 219 are connected to the supply oil circuit 122b be formed in MG1 lid 217 and housing 122.Supply oil circuit 122b is supplied to the oil pressure for control clutch C1 and drg B1 from valve body (not shown).
Following ball-bearing casing 120 is attached to the side surface on the rear side of MG1 lid 217: this ball-bearing casing is for supporting the front end of the rotor 2a of the first motor generator 2.Particularly, the outer ring 120a of ball-bearing casing 120 is fixed to MG1 lid 217.By the housing 122 that the MG lid 217 being fixed to protecgulum 208 as individual is attached to accommodation first motor generator 2, rotor 2a is incorporated to the inner ring 120b of ball-bearing casing 120.
As mentioned above, forming the component of change gear mechanism 17, as planetary gear unit 17b, power-transfer clutch C1, drg B1, input shaft 200 and tween drive shaft 201, be incorporated to protecgulum 208 and with MG1 lid 217 cover states under, change gear mechanism 17 is formed as individual unit.That is, the change gear mechanism 17 in the present invention can be formed as the variable gear unit covered with protecgulum 208 and MG1 lid 217, and this variable gear unit can be counted as subcomponent.
Housing 122 for holding the first motor generator 2, magslip 121 etc. is arranged in the rear side of the protecgulum 208 and MG1 lid 217 holding change gear mechanism 17.That is, the change gear mechanism 17 that holds described above covers with the protecgulum 208 and MG1 that form variable gear unit the front side that 217 are fixed to housing 122.Such as, as illustrated in figure 13, protecgulum 208, MG1 lid 217 and housing 122 are fixed to individual by multiple screw 123.Cover the structure on the rear side of 217 at protecgulum 208 and MG1, the structure namely on the rear side of housing 122 is identical with the structure gone out illustrated in Figure 12.
The fitting process of the torque transfer TM that Figure 12 or Figure 13 illustrates will be described below.First, bearing 124 and magslip 121 are attached to the inside of housing 122.Subsequently, the stator 2c of the first motor generator 2 is attached.Then, the rotor 2a of the first motor generator 2 is incorporated in the inner peripheral portion of stator 2c.
Be attached in housing 122 independent of magslip 121 or the first motor generator 2, variable gear unit is assembled.That is, power-transfer clutch C1 and drg B1 is attached to the inside of protecgulum 108.Subsequently, be attached planetary gear unit 17a, input shaft 100 and export flange 101.So attachment MG1 lid 118, to cover protecgulum 108.Thus, under the state that change gear mechanism 17 covers with protecgulum 108 and MG1 lid 118, change gear mechanism 17 is assembled into variable gear unit.Selectively, planetary gear unit 17b, input shaft 200 and tween drive shaft 201 are attached to the inside of protecgulum 208.Subsequently, power-transfer clutch C1 and drg B1 is attached.So attachment MG1 lid 217, to cover protecgulum 208.Thus, under the state that change gear mechanism 17 covers with protecgulum 208 and MG1 lid 217, change gear mechanism 17 is assembled into variable gear unit.
Variable gear unit, that is, the change gear mechanism 17 being attached to the change gear mechanism 17 in protecgulum 108 and MG1 lid 118 or being attached in protecgulum 208 and MG1 lid 217, is attached in the housing 122 of accommodation magslip 121 and the first motor generator 2.That is, variable gear unit (change gear mechanism 17 is incorporated to wherein) is attached to the left side of the housing 122 in Figure 12 or Figure 13.
Under the state that variable gear unit is attached in housing 122 as described above, the first motor generator 2 can be checked.Particularly, have identical castellated shaft 127a dummy shaft (dummyshaft) (not shown) replace have the power splitting mechanism 4 being formed with splined hole 127a flange 127 and be coupled to the rotor 2a at the first motor generator 2 rear end (right side in Figure 12, Figure 13) place formed splined hole 2d.By dummy shaft is connected to predetermined measuring apparatus, thus cause the first motor generator 2 shaft down, the running of the first motor generator 2 can be detected, easily regulate magslip 121 etc.
Power splitting mechanism 4 is attached to housing 122, and variable gear unit is attached to this housing 122.Particularly, power splitting mechanism 4 is attached from the right side of the housing 122 of Figure 12 or Figure 13.In power splitting mechanism 4, input shaft 125, flange 127, output shaft 126 etc. are attached to planetary gear unit in advance.The input shaft 125 of power splitting mechanism 4 inserts and is attached in the inner peripheral portion of the rotor 2a of the first motor generator 2 of housing 122.Be formed in the castellated shaft 125a in the input shaft 125 and splined hole 101a be formed in the output flange 101 of change gear mechanism 17 to be fitted to each other by spline.Selectively, be formed in the castellated shaft 125a in the input shaft 125 and splined hole 201a be formed in the tween drive shaft 201 of change gear mechanism 17 to be fitted to each other by spline.That is, the output link of change gear mechanism 17 and the input link of power splitting mechanism 4 are connected to each other by spline.
After this, casing 130 is attached to the rear end of housing 122.By casing 130 is attached to housing 122, the output shaft 126 of power splitting mechanism 4 is supported, and completes the assembling of torque transfer TM.
As mentioned above, according in torque transfer TM of the present invention, be arranged between driving engine 1 and power splitting mechanism 4 for the change gear mechanism 17 changing the rotating speed of driving engine 1.In torque transfer TM, the output link of change gear mechanism 17 and the input link of power splitting mechanism 4 are connected to each other by spline (or sawtooth).Thus, according in torque transfer TM of the present invention, when assembling torque transfer TM, relatively move along rotation axis direction by causing power splitting mechanism 4 and change gear mechanism 17, easily can connect power splitting mechanism 4 and change gear mechanism 17, to make transmission of power become possibility.
Particularly, according in torque transfer TM of the present invention, change gear mechanism 17, input link, output link etc. are assembled to housing 122 as single variable gear unit, and this housing holds power splitting mechanism 4, first motor generator 2 etc. and is the pith of torque transfer TM.Thus, by the variable gear unit holding change gear mechanism 17 is attached to from the rear side on rotation axis direction the housing 122 holding power splitting mechanism 4, first motor generator 2 etc., housing 122 and variable gear unit can easily be attached to each other.
In the case, as mentioned above, spline (or sawtooth) is formed in the connecting bridge between the output link and the input link of power splitting mechanism 4 of change gear mechanism 17.Thus, the input link of the output link of change gear mechanism 17 and power splitting mechanism 4 can easily and be satisfactorily engaged with each other.As a result, assembling or the capacity rating of the torque transfer TM comprising change gear mechanism 17 and power splitting mechanism 4 can be improved.
In instantiation mentioned above, comprise and be described to as driving engine 1, first motor generator 2 of drive source and the so-called two electric machine mixed power vehicles of the second motor generator 3 motor vehicle driven by mixed power that the present invention is applied to, but, such as, the motor vehicle driven by mixed power of the motor generator comprising driving engine and more than three can be adopted.The so-called plug-in hybrid vehicle that storage battery directly can charge with external power supply can be adopted.

Claims (7)

1., for a torque transfer for motor vehicle driven by mixed power, described motor vehicle driven by mixed power comprises as the driving engine of drive source and at least one whirler, and described torque transfer comprises:
Power splitting mechanism, it is made up of differential apparatus, and described power splitting mechanism is configured to distribute between described drive source and axle drive shaft or synthesize and transferring power, and described differential apparatus comprises three rotating elements, and described three rotating elements comprise:
First rotating element, it is connected to the first input link,
Second rotating element, it is connected to described whirler, and
3rd rotating element, it is connected to described axle drive shaft via the first output link; And
Change gear mechanism, it is configured to the rotating speed of the described driving engine changed via the second input link input, described change gear mechanism is configured to transmission of torque extremely described first input link and described first rotating element via the second output link, described change gear mechanism and described power splitting mechanism are arranged on the rotation axis identical with the output shaft of described driving engine, described change gear mechanism and described power splitting mechanism arrange with the order of described change gear mechanism and described power splitting mechanism in that side of described driving engine from closer, and described second output link and described first input link are connected to each other by spline and sawtooth.
2. torque transfer according to claim 1, comprises further:
Protecgulum, it covers the described engine side of described change gear mechanism;
Rotate cover, it covers the described power splitting mechanism side of described change gear mechanism; And
Housing, it holds described power splitting mechanism and described whirler, wherein
Described change gear mechanism is accommodated in described protecgulum, and described change gear mechanism is covered by described protecgulum and described rotation cover,
Described change gear mechanism, described protecgulum and described rotation cover form variable gear unit,
Described second input link is supported by described protecgulum and described first input link or described second input link is supported by described protecgulum and described second output link, and
Described variable gear unit is attached to the end on described change gear mechanism side of described housing.
3. torque transfer according to claim 1 and 2, wherein said second output link comprises flange member, described flange member is arranged in the end on described power splitting mechanism side of described second output link, and described flange member comprises one in splined hole, sawtooth hole, castellated shaft and derrated shaft, and
Described first input link comprises shaft component, described shaft component is arranged in the end on described change gear mechanism side of described first input link, and described shaft component supports the end on described power splitting mechanism side of described second input link to rotate relative to described first input link, and described shaft component comprises the component come from following four components corresponding to described flange member:
Castellated shaft, it coordinates with the described splined hole of described second output link;
Derrated shaft, it coordinates with the described sawtooth hole of described second output link;
Splined hole, it coordinates with the described castellated shaft of described second output link; And
Sawtooth hole, it coordinates with the described derrated shaft of described second output link.
4. torque transfer according to claim 1 and 2, wherein said second output link comprises the second shaft component, described second shaft component is arranged in the end on described power splitting mechanism side of described second output link, and described second shaft component comprises one in splined hole, sawtooth hole, castellated shaft and derrated shaft, and the part in the described power splitting mechanism of described second input link of described shaft component support is relatively to rotate, and
Described first input link comprises the first shaft component, described first shaft component is arranged in the end on described change gear mechanism side of described first input link, and described first shaft component comprises the component come from following four components corresponding to described second shaft component:
Castellated shaft, it coordinates with the described splined hole of described second output link;
Derrated shaft, it coordinates with the described sawtooth hole of described second output link;
Splined hole, it coordinates with the described castellated shaft of described second output link; And
Sawtooth hole, it coordinates with the described derrated shaft of described second output link.
5. torque transfer according to any one of claim 1 to 3, wherein said change gear mechanism comprises:
Planetary gear unit, it is single planetary gear unit and comprises pinion carrier, internally toothed annulus and sun wheel;
Power-transfer clutch, it makes described sun wheel optionally be connected each other with described pinion carrier; And
Drg, it optionally fixes described sun wheel so that non rotating,
Described internally toothed annulus is connected to described second output link to rotate together,
Described pinion carrier is connected to described second input link to rotate together, and
The described end on described power splitting mechanism side of described second input link is supported relatively to rotate by the inner peripheral portion of the described end on described change gear mechanism side of described first input link.
6. the torque transfer according to any one of claim 1,2 and 4, wherein said change gear mechanism comprises:
Planetary gear unit, it is dual planetary gear unit and comprises pinion carrier, internally toothed annulus and sun wheel;
Power-transfer clutch, it makes described sun wheel optionally be connected each other with described pinion carrier; And
Drg, it optionally fixes described sun wheel so that non rotating,
To rotate relative to described sun wheel in the inner peripheral portion that described second output link is arranged in described sun wheel,
Described pinion carrier is connected to described second output link to rotate together,
Described internally toothed annulus is connected to described second input link to rotate together, and
The described end on described power splitting mechanism side of described second input link is supported relatively to rotate by the inner peripheral portion in described engine side of described second output link.
7. torque transfer according to any one of claim 1 to 6, wherein said whirler comprises inner rotor motor, described inner rotor motor comprises the rotor with hollow structure, described whirler is arranged on the rotation axis identical with the described output shaft of described driving engine, and described whirler is arranged between described change gear mechanism and described power splitting mechanism
Described first input link is supported relatively to rotate by the inner peripheral portion of described rotor, and
Described second output link and described first input link are connected to each other in the inner peripheral portion of described inner rotor motor.
CN201480050391.6A 2013-09-13 2014-09-11 Power transmission for motor vehicle driven by mixed power Expired - Fee Related CN105531135B (en)

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PCT/IB2014/001787 WO2015036838A1 (en) 2013-09-13 2014-09-11 Power transmitting apparatus for hybrid vehicle

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JP2015054683A (en) 2015-03-23
JP6135418B2 (en) 2017-05-31
WO2015036838A1 (en) 2015-03-19
US9944164B2 (en) 2018-04-17
US20160214473A1 (en) 2016-07-28

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